US5100211A - Hydraulic braking pressure control system - Google Patents

Hydraulic braking pressure control system Download PDF

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Publication number
US5100211A
US5100211A US07/611,575 US61157590A US5100211A US 5100211 A US5100211 A US 5100211A US 61157590 A US61157590 A US 61157590A US 5100211 A US5100211 A US 5100211A
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US
United States
Prior art keywords
valve
chamber
control
sleeve
valve seat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/611,575
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English (en)
Inventor
Yoichi Sugimoto
Kougyoku Go
Yoshihiro Iwagawa
Etsuo Fujii
Naotoshi Tamai
Atsushi Shimizu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Nissin Kogyo Co Ltd
Original Assignee
Honda Motor Co Ltd
Nissin Kogyo Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honda Motor Co Ltd, Nissin Kogyo Co Ltd filed Critical Honda Motor Co Ltd
Assigned to HONDA GIKEN KOGYO KABUSHIKI KAISHA, NISSIN KOGYO KABUSHIKI KAISHA reassignment HONDA GIKEN KOGYO KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: FUJII, ETSUO, GO, KOUGYOKU, IWAGAWA, YOSHIHIRO, SHIMIZU, ATSUSHI, SUGIMOTO, YOICHI, TAMAI, NAOTOSHI
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/42—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems
    • B60T8/4208—Debooster systems
    • B60T8/4225—Debooster systems having a fluid actuated expansion unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/88—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration with failure responsive means, i.e. means for detecting and indicating faulty operation of the speed responsive control means
    • B60T8/92—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration with failure responsive means, i.e. means for detecting and indicating faulty operation of the speed responsive control means automatically taking corrective action
    • B60T8/94—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration with failure responsive means, i.e. means for detecting and indicating faulty operation of the speed responsive control means automatically taking corrective action on a fluid pressure regulator

Definitions

  • the present invention relates to a hydraulic braking pressure control system in which an output chamber and a control chamber are defined in a housing with opposite ends of a control piston facing them, respectively.
  • the output chamber leads to a brake device, while the control chamber is connected to a control hydraulic pressure source and a reservoir through a switchover valve means capable of changing over the connection and disconnection.
  • a cut-off valve is interposed between an input chamber defined in the housing and connected to a master cylinder and the output chamber, and is adapted to be closed in response to the movement of the control piston toward the control chamber.
  • Japanese Patent Application Laid-open No. 107435/85 discloses a hydraulic braking pressure control system in which the control chamber is tightly closed when control hydraulic pressure is abnormally reduced.
  • the cut-off valve is permitted to be closed, and a passage connecting the input chamber and the output chamber to bypass the cut-off valve is opened. Therefore, such a passage and a means for opening and closing the passage are required in addition to the cut-off valve, resulting in a complicated construction.
  • the present invention has been accomplished with such circumstances in view, and it is an object of the present invention to provide a hydraulic braking pressure control system wherein the opening of the cut-off valve and the tight closing of the control chamber upon the abnormal reduction of control hydraulic pressure can be achieved with a simplified construction.
  • the present invention includes a hydraulic braking pressure control system having an output chamber connected to a brake device and a control chamber connected to a control hydraulic pressure source and a reservoir through a switchover valve means capable of changing over the connection and disconnection with the chambers being defined in a housing by a control piston.
  • a cut-off valve is interposed between an input chamber defined in the housing and connected to a master cylinder and the output chamber and is adapted to be closed in response to the movement of the control piston toward the control chamber.
  • a sleeve is slidably received in the slide bore of the housing and has a larger diameter portion facing the output chamber to define a pilot chamber between the sleeve and a step in the slide bore.
  • the pilot chamber is connected to the control hydraulic pressure source.
  • the control piston is slidably received in the sleeve, with one end of the control piston facing the output chamber and the other end facing the control chamber.
  • a lock valve is interposed between the control chamber and the switchover valve means and adapted to be closed in response to the movement of the sleeve in a direction to reduce the volume of the pilot chamber.
  • the cut-off valve between the input chamber and the output chamber includes a valve seat member having a valve bore and axially movably disposed in the housing with one of opposite ends of the valve seat member abutting against an end face of the larger diameter portion of the sleeve and with the opposite ends of the valve seat member facing the input chamber and the output chamber, respectively, a valve member disposed at a location closer to the input chamber and able to seat on a valve seat which is provided on the valve seat member to surround that open end of the valve bore which is closer to the input chamber, the valve member being biased by a spring in a direction to seat on the valve seat, and a stopper fixedly disposed in the housing to regulate the maximum amount of movement of the valve member in a seating direction to a position of the valve member spaced apart from the valve seat when the valve seat member is moved to the maximum extent in response to the movement of the sleeve in a direction to reduce the volume of the pilot chamber.
  • control hydraulic pressure from the control hydraulic pressure source is abnormally reduced, then the sleeve and the control piston are moved in a direction to increase the volume of the output chamber in response to application of the hydraulic braking pressure from the master cylinder to the output chamber, and the valve seat member and the valve member are moved by the hydraulic pressure in the input chamber.
  • the lock valve is closed and at the same time, in the cut-off valve, the valve seat member is moved in a manner to follow the sleeve even after the movement of the valve member is regulated by the stopper, thus opening the cut-off valve.
  • the single FIGURE is a longitudinal sectional view illustrating one embodiment of the present invention.
  • a hydraulic braking pressure control system 3 is interposed between a master cylinder 1 and a brake device 2.
  • the hydraulic braking pressure control system 3 is capable of transmitting hydraulic braking pressure delivered through an output port 1a in the master cylinder 1 in response to the depressing of a brake pedal 4 during a normal braking and controlling the hydraulic braking pressure applied to the brake device in response to the controlling of the operation of a switchover valve means 5 during an anti-lock brake control.
  • the brake device 2 comprises a cylinder 6 and a braking piston 7 slidably received in the cylinder 6 and is adapted to exert a braking force by the hydraulic braking pressure applied to a hydraulic braking pressure chamber 8 defined between the cylinder 6 and the braking piston 7.
  • a housing 9 of the hydraulic braking pressure control system 3 is provided with a slide bore 10 which is comprised of, in sequence from one end (lower end as viewed in the FIGURE) side of the housing, a larger diameter bore portion 10a opened at one end into one end face of the housing 9, and a smaller diameter bore portion 10b coaxially connected at one end to the other end of the larger diameter bore portion 10a through a step 10c.
  • One end of the slide bore 10, i.e., the opened end of the larger diameter bore portion 10a is closed by an end plate 11 secured to the housing 9.
  • the housing 9 is provided with a bottomed engagement hole 12 which has a smaller diameter than that of the smaller diameter bore portion 10b and is coaxially connected to the end of the slide bore 10, i.e., the other end of the smaller diameter bore portion 10b through a step 13.
  • a sleeve 14 is slidably received in the slide bore 10 and comprised of a larger diameter portion 14a corresponding to the larger diameter bore portion 10a and a smaller diameter portion 14b corresponding to the smaller diameter bore portion 10b, the larger and smaller diameter portions 14a and 14b being coaxially connected to each other.
  • a seal member 18 is fitted in an outer surface of the larger diameter portion 14a in slide contact with an inner surface of the larger diameter bore portion 10a.
  • a seal member 19 is fitted in an outer surface of the smaller diameter portion 14b in slide contact with an inner surface of the smaller diameter bore portion 10b.
  • An annular pilot chamber 15, facing the step 10c of the slide bore 10, is defined between an outer surface of the sleeve 14 and an inner surface of the slide bore 10.
  • the pilot chamber 15 is connected to a control hydraulic pressure source 17 through a passage 16 provided in the housing 9.
  • the control hydraulic pressure source 17 comprises a hydraulic pump 21 for pumping a control liquid from a reservoir 20, an accumulator 22 connected to the hydraulic pump 21, and a pressure switch 23 for controlling the operation of the hydraulic pump 21.
  • a control hydraulic given pressure higher than the hydraulic braking pressure delivered from the master cylinder 1 can be supplied from the control hydraulic pressure source 17.
  • a cylinder bore 24 opening in an end face of the larger diameter portion 14a of the sleeve 14, a communication hole 25 having a diameter smaller than that of the cylinder bore 24, and a support hole 26 having a diameter larger than that of the communication hole 25 and opening in an end face of the smaller diameter portion 14b.
  • a control piston 28 is slidably received in the cylinder bore 24 to define a control chamber 27 between the control piston 28 and the sleeve 14.
  • a lock valve 30 is interposed between the control chamber 27 and a passage 29 provided in the farthest end of the housing 9.
  • the switchover valve means 5 is interposed between the passage 29 and the control hydraulic pressure source 17 as well as the reservoir 20.
  • the switchover valve means 5 is comprised of a normally-open type solenoid valve 31 interposed between the passage 29 and the control hydraulic pressure source 17, and a normally-closed type solenoid valve 32 interposed between the passage 29 and the reservoir 20, so that the change-over of the energization and deenergization of the solenoid valves 31 and 3 enables the change-over between a condition in which the passage 29 is in communication with the control hydraulic pressure source 17, a condition in which the passage 29 is in communication with the reservoir 20, and a condition in which the passage 29 is out of communication with the control hydraulic pressure source 17 and the reservoir 20.
  • the lock valve 30 comprises a valve seat member 34 fitted in the engagement hole 12 in the housing 9 and having a valve bore 33 communicating with the passage 29, a valve member 36 seatable on the valve seat 35 provided on the valve seat member 34 at the open end of the valve bore 33 closer to the sleeve 14, and a valve spring 37 for biasing the valve member 36 in a direction to seat on the valve seat 35.
  • a basically cylindrical retainer 38 is press-fitted in the support hole 26 provided in the sleeve 14.
  • a radially inwardly projecting flange 39 is provided on the end of the retainer 38 closer to the valve seat member 34.
  • the valve member 36 is disposed to extend through the flange 39.
  • Receiving collars 40 capable of abutting against the flange 39 are projectingly provided on a side of the valve member 36 at a plurality of circumferentially spaced apart locations.
  • the valve spring 37 is mounted and compressed between the receiving collars 40 and the sleeve 14.
  • valve member 36 with the receiving collars 40 in abutment against the flange 39 is in a position spaced apart from the valve seat 35.
  • the valve member 36 would then seat on the valve seat 35 in response to the movement of the sleeve 14 toward the valve seat member 34 in accordance with the reduction of the control hydraulic pressure in the pilot chamber 15.
  • a basically cylindrical guide member 42 is received in the larger diameter bore portion 10a in the housing 9 at a location closer to the end plate 11
  • An output chamber 41 is defined between the guide member 42, the end face of the larger diameter portion 14a of the sleeve 14 and one end of the control piston 28.
  • the output chamber 41 is connected to the brake device 2 through a passage 43 provided in the housing 9.
  • An input chamber 45 is defined in the guide member 42 and connected to the output port 1a in the master cylinder 1 through a passage 44 provided in the housing 9.
  • a cut-off valve 46 is interposed between the input chamber 45 and the output chamber 41.
  • the cut-off valve 46 comprises a valve seat member 48 having a valve bore 47 coaxial with the sleeve 14 and axially slidably received in the guide member 42, a valve member 50 seatable on a valve seat 49 provided on the valve seat member 48 to surround the open end of the valve bore 47 closer to the input chamber 45, a valve spring 51 for biasing the valve member 50 in a direction of seating on the valve seat 49, and a stopper 52 provided on the guide member 42 to regulate the maximum amount of movement of the valve member 50 in the direction to seat on the valve seat 49.
  • the stopper 52 is provided on an inner surface of the guide member 42 to project radially inwardly therefrom.
  • a bottomed cylindrical lid member 53 is received in the guide member 42 and is clamped by the stopper 52 and the end plate 11.
  • the valve seat member 48 is comprised of a cylindrical portion 48a received liquid-tightly and slidably in the guide member 42 from the side of the output chamber 41, and a disk portion 48b integrally provided on an end of the cylindrical portion 48a so that one end can abut against an end face of the guide member 42 in the output chamber 41 and the other end can abut against the end face of the larger diameter portion 14a of the sleeve 14 as well as one end face of the control piston 28.
  • the length of the cylindrical portion 48a is set so that a space is provided between a leading end of the cylindrical portion 48a and the stopper 52 when the disk portion 48b is in abutment against the guide member 42.
  • the input chamber 45 is defined between the leading end of the cylindrical portion 48a and the lid member 53 in the guide member 42.
  • the valve member 50 is provided with a regulating collar 50a abuttable against the stopper 52.
  • a driving rod 50b is connected on the valve member 50 passing loosely through the valve bore 47 to be able to abuts against one end face of the control piston 28.
  • the valve spring 51 is mounted in a compressed manner between the regulating collar 50a and the lid member 53. The valve spring 51 does not have a spring force enough to overcome the friction resistance of sliding movement of the control piston 28 in the cylinder bore 24.
  • the stopper 52 for regulating the maximum amount of movement of the valve member 50 in the direction to seat on the valve seat 49 is disposed such that the valve member 50 with the regulating collar 50a in abutment against the stopper 52 is in a position spaced apart from the valve seat 49 when the valve seat member 48 has been moved to the maximum extent toward the sleeve 14 in response to the movement of the sleeve 14 in a direction to reduce the volume of the pilot chamber 15.
  • valve seat member 48 of the cut-off valve 46 has the disk portion 48b thereof clamped between the sleeve 14 as well as the control piston 28 and the guide member 42.
  • the valve member 50 of the cut-off valve 46 is in an opened position spaced apart from the valve seat 49 as a result of the driving rod 50b being urged by the control piston 28.
  • the normally-open type solenoid valve 31 and the normally-closed type solenoid valve 32 of the switchover valve means 5 are energized. This causes the control chamber 27 to be put into communication with the reservoir 20 and thus reduced in pressure. Therefore, the control piston 28 is moved by the hydraulic pressure from the output chamber 41 in a direction to increase the volume of the output chamber 41, thereby the reducing the braking force in the brake device 2.
  • the normally-closed type solenoid valve 32 When the braking force is to be maintained, the normally-closed type solenoid valve 32 may be deenergized with the normally-open type solenoid valve 31 energized, thereby shutting off the communication of the control chamber 27 with the reservoir 20, so that the control piston 28 may be maintained at a given position. Further, when the braking force is to be increased again, both of the normally-open type solenoid valve 31 and the normally-closed type solenoid valve 32 may be deenergized. This enables the braking force of the brake device 2 to be increased by application of the control hydraulic pressure from the control hydraulic pressure source 17 to the control chamber 27.
  • the cut-off valve 46 is in its opened state. If the hydraulic braking pressure from the master cylinder 1 is applied to the input chamber 45 in response to the braking operation, such hydraulic braking pressure is applied to the output chamber 41 through the valve bore 47, thereby urging the control piston 28 and the sleeve 14 in the direction to increase the volume of the output chamber 41. The valve member 50 of the cut-off valve 46, moves to follow the movement of the control piston 28, thus seating on the valve seat 49, thereby closing the cut-off valve 46.
  • the hydraulic pressure from the input chamber 45 is applied directly to the valve member 50 and the valve seat member 48, so that the valve member 50 and the valve seat member 48 are urged toward the output chamber 41 while urging the sleeve 14 and the control piston 28 in a condition in which the hydraulic pressure in the pilot chamber 15 and the control chamber 27 is reduced.
  • the maximum amount of movement of the valve member 50 toward the output chamber 41 is regulated by the stopper 52, whereas an acceptable amount of movement of the valve seat member 48 toward the output chamber 41 is larger than the amount of movement of the valve member 50 regulated by the stopper 52. Therefore, the valve seat 49 moves away from the valve member 50, resulting in the cut-off valve 46 being opened. Accordingly, the hydraulic braking pressure from the master cylinder 1 can be applied to the brake device 2 to insure the braking force.
  • the lock valve 30 is closed prior to opening of the cut-off valve 46, thereby avoiding any problem that the hydraulic pressure from the control chamber 27 is released more than necessary. This ensures that the volume of the output chamber 41 cannot be increased more than necessary, and the braking force can be easily insured in the brake device 2.
  • the lock valve when the control hydraulic pressure is abnormally reduced, the lock valve is closed to bring the control chamber into a tightly closed state and the same time, the cut-off valve is opened by the movement of the sleeve in the direction to reduce the volume of the pilot chamber in response to application of the hydraulic braking pressure from the master cylinder to the output chamber. This enables the braking force to be insured in the brake device.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)
US07/611,575 1989-11-14 1990-11-13 Hydraulic braking pressure control system Expired - Fee Related US5100211A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP1-132318[U] 1989-11-14
JP1989132318U JPH081167Y2 (ja) 1989-11-14 1989-11-14 制動液圧制御装置

Publications (1)

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US5100211A true US5100211A (en) 1992-03-31

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US07/611,575 Expired - Fee Related US5100211A (en) 1989-11-14 1990-11-13 Hydraulic braking pressure control system

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US (1) US5100211A (fi)
JP (1) JPH081167Y2 (fi)
GB (1) GB2238837B (fi)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5174635A (en) * 1990-09-25 1992-12-29 Nissin Kogyo Co., Ltd. Hydraulic braking pressure control system for rear wheel brake
US5306075A (en) * 1990-10-26 1994-04-26 Honda Giken Kogyo Kabushiki Kaisha Hydraulic braking pressure control system having an on-off valve responsive to an output hydraulic pressure

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1421703A (en) * 1973-04-03 1976-01-21 Dba Sa Hydraulic pressure modulatorp
US4017126A (en) * 1975-10-28 1977-04-12 Tokico Ltd. Vehicle anti-skid braking device
US4322114A (en) * 1979-01-12 1982-03-30 Akebono Brake Industry Co., Ltd. Hydraulic pressure control device for double hydraulic piping for vehicle brakes
GB2163821A (en) * 1984-07-17 1986-03-05 Honda Motor Co Ltd Anti-skid vehicle braking system
US4890891A (en) * 1986-11-06 1990-01-02 Daimler-Benz Aktiengesellschaft Antilock system for a road vehicle
US4929036A (en) * 1988-06-24 1990-05-29 Honda Giken Kogyo Kabushiki Kaisha Hydraulic brake pressure control device for a vehicle

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5516855B2 (fi) * 1971-11-01 1980-05-07
JPS5889466U (ja) * 1981-12-14 1983-06-17 トキコ株式会社 アンチスキツド機構

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1421703A (en) * 1973-04-03 1976-01-21 Dba Sa Hydraulic pressure modulatorp
US4017126A (en) * 1975-10-28 1977-04-12 Tokico Ltd. Vehicle anti-skid braking device
US4322114A (en) * 1979-01-12 1982-03-30 Akebono Brake Industry Co., Ltd. Hydraulic pressure control device for double hydraulic piping for vehicle brakes
GB2163821A (en) * 1984-07-17 1986-03-05 Honda Motor Co Ltd Anti-skid vehicle braking system
US4890891A (en) * 1986-11-06 1990-01-02 Daimler-Benz Aktiengesellschaft Antilock system for a road vehicle
US4929036A (en) * 1988-06-24 1990-05-29 Honda Giken Kogyo Kabushiki Kaisha Hydraulic brake pressure control device for a vehicle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5174635A (en) * 1990-09-25 1992-12-29 Nissin Kogyo Co., Ltd. Hydraulic braking pressure control system for rear wheel brake
US5306075A (en) * 1990-10-26 1994-04-26 Honda Giken Kogyo Kabushiki Kaisha Hydraulic braking pressure control system having an on-off valve responsive to an output hydraulic pressure

Also Published As

Publication number Publication date
JPH0370563U (fi) 1991-07-16
JPH081167Y2 (ja) 1996-01-17
GB2238837B (en) 1993-11-10
GB2238837A (en) 1991-06-12
GB9024769D0 (en) 1991-01-02

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Owner name: NISSIN KOGYO KABUSHIKI KAISHA, JAPAN

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